JPH038821A - Rotary ring for spinning - Google Patents

Abstract

PURPOSE:To obtain the title device preventing excessive high speed of ring rotator and having high productivity, equipped with a brake shoe to transform by centrifugal force at the lower part of the ring rotator and a brake ring coming into contact with a sliding part at the bottom face of a holder by the transformation. CONSTITUTION:In a rotary ring 1 for spinning having a holder 11 and a ring rotator 13 rotatably supported through a bearing part 12 by the holder 11, a brake shoe 28 comprising an elastic material to transform by centrifugal force by rotation is set at the lower part of the ring rotator 13 and a brake ring 61 which is constituted in such a way that the brake ring is brought into contact with a sliding part 47 laid at the bottom face of the holder 11 by transformation of the brake shoe 28 and is supported by the brake shoe 28 to control the rising limit of number of revolutions of the ring, to suppress rotation of inertia during suspension and to carry out spinning in good productivity.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a spinning spinning ring of a passive rotation type in which a ring rotating body rotates using sliding friction caused by the rotation of a traveler as torque, and particularly to a brake mechanism thereof.

[Conventional technology and its problems]

Conventionally, a rotating ring for spinning has a ring rotating body that is rotatably supported by a holder via a bearing part, and the ring rotating body is configured to rotate using the sliding friction force generated by the rotation of a traveler as torque. , Special Public Service 1977-1
This is known from Japanese Patent No. 5934 and the like.

In addition, for the passive rotating ring of such a mechanism, as a known mechanism to prevent ring overrun when the machine is stopped, wings or protrusions are provided on the ring rotating body, and the ring rotation is caused by fluid resistance such as air or liquid. There is a rotation control mechanism that suppresses the rotation of the ring body, or a brake mechanism that mechanically applies pinching friction to the ring rotating body through a mechanism such as a lever to prevent inertial rotation of the ring rotating body.

Among these mechanisms, in the mechanism in which air friction vanes are provided on the ring rotating body to control the ring rotation, it becomes difficult to prevent the ring from overrunning if the ring rotation speed increases and the inertial rotational force increases. In addition, there is a mechanism in which wings or protrusions are protruded from the lower end of the ring rotating body to lift up the oil tank etc. when the machine is stopped, and the ring rotating body is braked by the resistance of the liquid, and the lower end of the ring rotating body is protruded from the back of the ring rail. All brake mechanisms that directly apply squeezing friction to the protruding part of the ring via a lever or the like are designed to stop the ring rotation of all machines at the same time. During the spinning process other than that, there may be damage to individual rings, burnout due to individual differences in traveler wear, biting, changes in stretch length due to pinching motion, lifting and lowering of ring rail between chisels, etc. When the spinning tension is instantaneously fluctuated due to a shock or the variable speed rotation of the traveler, the air bearing or thrust bearing draws a J-curve in a short period of time due to the lifting tension to reach the same speed as the traveler, and the speed between the chaser and the The inventor of the present invention has discovered through research that it is synchronized with the maximum rotation speed of the traveler.

In this case, the ring rotation cannot change speed due to inertia in response to the chase-to-chase speed change of the traveler, so it repeats overrun and rotation at the same speed as the traveler rotation, resulting in severe abnormal fluctuations in the balloon tension. . However, as described above, the known braking methods for controlling ring rotation mainly involve simultaneous braking for the purpose of preventing overrun due to inertial rotation of the ring when the pipes are fully stopped, or the special method previously proposed by the present inventor. It was a contact brake system as seen in Japanese Patent Application No. 62-134382 and Special Publication No. 54-15934, but today's spinning machines have a spindle rotation of 20,000 to 25,000 R.
Although it is now possible to spin PM at high speed, and it is possible to automatically control the spindle rotation using an inverter or other means, as long as a passive rotating ring is used, which is a mechanism that rotates by the torque of the traveler, the spindle rotation cannot be completely controlled when the machine is stopped. In the spindle-simultaneous braking system, it is not possible to control the ring rotation of each spindle during spinning at variable speed. For this reason, as mentioned above, due to the repeated rapid tension fluctuations that occur in the weight where the maximum rotational speed between the traveler's chases and the ring rotational speed are synchronized, fluffing occurs, especially in pure synthetic fibers, high-grade varieties, and fine-count spinning. Problems that lead to deterioration of thread quality, such as shigokinep and weak threads, occur.

In addition, the direct contact type friction brake proposed earlier has sufficient effects in increasing the speed of the individual weight rings and preventing them from rotating synchronously with the traveler, but if the brake shoes are in full contact with the contact surface of the fixed holder at the same time, Due to the unique characteristics of the brake shoe material, hardness and elasticity, and gap size settings, the sum of friction torque remains constant, and the maximum rotational speed of the ring also remains constant due to the brake characteristics. As a result, even if the friction torque of the traveler increases due to further increase in spindle rotation, the brake torque of the brake shoes is infinitely greater, so the ring rotation will not follow the traveler torque and increase its speed (at the same time). In order to maintain the rotation speed, the deviation from the increasing curve of the spindle rotation gradually increases, resulting in an increase in the spinning tension, and when the limit spinning tension is reached, the spindle rotation increase limit is reached.

As a result, if the unique characteristics of the brake mechanism are set to match the friction brake operating point to the faster spindle rotation and raise the upper limit of ring rotation speed, for example, if the maximum spindle rotation speed is set to 20,000 RPM, the maximum ring rotation speed The number is 6
If the brake shoes are set to 12,000 PPM (0%), when the platform is stopped and decelerated, the stopping time due to inertial rotation of the ring will be longer than the spindle stopping time, and there is a danger that overrun and snarl will occur. Therefore, it is necessary to make the spindle deceleration curve long so as to reduce the inertia of the ring rotation and stop the platform after reducing the ring rotation to, for example, 6,000 to 5,000 RPM.

For this reason, it has become necessary to set a brake mechanism to limit the ring rotation to 7,000 to 6,000 PPM, which has resulted in restricting or reducing the speed-up performance of the spinning machine.

In view of the above-mentioned problems, the present invention aims to solve the problem of excessive speed increase caused by the use of an air bearing in the bearing part of a ring rotating body.
In particular, in order to prevent synchronization with the maximum traveler rotation, and to maintain a rotation difference that does not cause the ring rotation speed change curve to deviate excessively from the spindle rotation speed change curve, the individual weights are It is an object of the present invention to provide a rotating ring for spinning that can control the maximum rotation speed of the ring.

[Means for Solving the Problems] In order to solve the above-mentioned problems, the present invention provides a rotating ring for spinning comprising a holder and a ring rotating body rotatably supported by the holder via a bearing part. In,
A brake shoe made of an elastic body and a brake ring supported by the brake shoe are provided at the lower end of the ring rotating body, and the brake shoe is deformed by centrifugal force due to rotation of the brake shoe, and The brake ring is configured to come into contact with a sliding contact portion provided on a lower end surface of the holder as the brake shoe deforms.

(Function) As the ring rotating body rotates, the brake shoe also rotates, and the centrifugal force caused by this rotation causes the brake shoe to elastically deform, and the upper component of the centrifugal force lifts the peripheral edge using the bent portion as a fulcrum.

This deformation of the brake shoe causes the brake ring to move upward, and when the rotational speed reaches a certain speed, the brake ring comes into contact with the sliding contact area, and the contact pressure acts to pull down the ring rotating body, resulting in a The holder of the fixed part is pressed up and down at the contact surface between the part and the brake shoe, and a braking force is generated due to friction.

〔Example〕

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a cross-sectional front view of a spinning ring 1 according to the present invention, and FIG. 2 is a partially cross-sectional front view showing essential parts of the brake mechanism of the spinning spinning ring l of FIG.

The rotating ring 1 for spinning includes a holder 11 and a shaft bearing part 1.
and a ring rotating body 13 which is rotatably supported by a holder 11 via 2.

The ring rotating body 13 includes a flange rotor 21 on which the traveler 14 can slide and rotate, a lower rotor 22 that is fitted into the lower part of the inner peripheral surface of the flange rotor 21 and integrated, and a lower rotor 22 that is elastically fitted into the lower part of the inner peripheral surface of the lower rotor 22. brake shoe 28, a presser ring 25 for elastically fixing the brake shoe 28 to the lower rotor 22, and the brake shoe 28
It is composed of a brake ring 61 that is placed on top of the brake ring 61 and moves up and down, and a dust cover 20.

The bearing part 12 includes a groove 31 formed on the inner peripheral surface of the holder 11, a groove 32 formed on the outer peripheral surface of the ring rotating body 13 by the flange rotor 21 and the lower rotor 22,
It is composed of an annular slide ring 35 fitted between these grooves 31 and 32 with a small gap.

After the holder 11 is fitted into a mounting hole 42 of a ring rail 41, a stop ring 44 is fitted into a circumferential mounting groove 43 and fixed. A sliding contact portion 47 consisting of an annular horizontal surface is formed on the lower end surface of the holder 11 .

The brake ring 61 is made of a polymer resin (engineering plastic) with excellent heat resistance and wear resistance, for example,
It is formed in an annular shape from a material with a low coefficient of friction such as polyimide, polyamide-imide, carbon fiber, tetrafluoroethylene resin with various fillers, or fine ceramics, and the lower surface has a ring extending in the radial direction. Four to three engagement grooves 62 are provided radially at equal angles in the circumferential direction. Each engagement groove 62 is formed with a slope that is deeper on the inner circumferential side of the brake ring 61 than on the outer circumferential side,
The inner corner is formed into a smooth arc.

The brake shoe 28 is made of a soft elastic material such as synthetic rubber or synthetic resin, and includes a vertical portion 51, an inclined portion 56, and a bent portion 53 connecting these portions.

The vertical portion 51 has a substantially cylindrical shape, has a large number of protruding lines 51a on its outer circumferential surface, and fits into the inner circumferential surface of the lower rotor 22. The protrusion 51a engages with the retaining groove 22a, and
A rigid cylindrical holding ring 25 made of metal or the like is fitted into the inner peripheral surface of the vertical portion 51. The vertical portion 51 of the brake shoe 28 receives pinching pressure between the outer peripheral surface of the cylindrical holding ring 25 and the inner peripheral surface of the lower rotor 22, and is press-fitted into the lower rotor 22 so as not to come off.

The bent portion 53 has an arcuate cross-section constricted toward the center, and the inclined portion 56 constitutes an elastic curved portion that can be easily deformed outward and upward by the centrifugal force.

The inclined portion 56 includes a number of hemispherical support protrusions 71 for horizontally supporting the brake ring 61 by contacting the lower surface of the brake ring 61, and a plurality of hemispherical support protrusions 71 that fit into the engagement grooves 62 of the brake ring 61 to support the brake ring 61. A radial streak-like protrusion 72 engages to rotate the brake ring integrally with the brake ring, and an annular steady rest protrusion 73 having a triangular cross section and an outer diameter slightly larger than the inner diameter of the brake ring. Each support protrusion 71
are provided at regular angle intervals (for example, every 30 degrees) in the circumferential direction. When the ring rotating body 13 is stopped without rotating, that is, when it is in its free state, the inclined portion 56 opens outward and diagonally downward, and the angle α between its surface and the horizontal plane is is between 30 degrees and 60 degrees.

When the ring rotating body 13 rotates, the brake shoe 28 also rotates, and the peripheral edge of the inclined portion 56 opens in a fan shape around the bent portion 53 due to the centrifugal force, and attempts to become horizontal due to the component of the centrifugal force. The brake ring 61 is elastically deformed so as to be lifted up, thereby causing the brake ring 61 to press against the support protrusion 71.
It is supported by and lifted upward. The amount of deformation of the inclined portion 56 increases according to the rotational speed of the ring rotary body 13, and therefore the upward movement amount of the brake ring 61 also increases according to the rotational speed of the ring rotary body 13.

When the rotational speed increases to a certain value and the angle between the inclined portion 56 and the horizontal surface becomes β, the upper surface of the brake ring 61 contacts and is pressed against the sliding portion 47, as shown in FIG. As a result, a frictional force is generated between the brake ring 61 and the sliding contact portion 47, and a braking force is applied.

In addition, the force of pressing the brake ring 61 against the sliding contact portion 47 increases according to the rotational speed of the ring rotating body 13, and a force that pulls down the ring rotating body 13 acts, causing friction on the sliding surface of the bearing portion 12. Since pressure is applied and the holder 11 of the fixed part is compressed via the slide ring 35, the braking force is also increased.

Next, the operation of the rotating spinning ring l configured as described above will be explained in more detail.

The traveler 14 rotates due to the rotation of the spindle, and the ring rotating body 13 rotates using the sliding frictional force with the traveler 14 as torque. At the same time, the brake shoe 28 rotates together.

The brake ring 61 is simultaneously supported at multiple points on the same radius by the support protrusions 71 of the brake shoe 28 so as to be in a horizontal state, and as the brake shoe 28 rotates, the brake ring 61 similarly moves while maintaining the horizontal state. Rotate. At this time, the inner peripheral surface of the brake ring 61 is guided by the steady rest protrusion 73 so that the center point of the brake ring 61 becomes the center of rotation, and the initial center runout of the brake ring 61 due to rotation is prevented.

When the inclined part 56 is lifted upward by the rotation of the brake shoe 28, the brake ring 61 also initially moves to the inclined part 5.
The brake ring 61 is then lifted up in the same manner along the tapered inclined surface of the brake ring 6, supported by the support protrusion 71, and when the rotational speed reaches a certain set speed, the rotation of the brake ring 61 is caused by its own centripetal force to rotate around the outer periphery of the support protrusion 71. Ring rotating body 1 away from the surface
3, the brake ring 61 performs a concentric rotational movement with no center runout, and the upper surface of the brake ring 61 comes into contact with the sliding contact portion 47.

That is, as the speed of the ring rotating body 13 increases, the brake ring 61 gradually comes into close contact with the sliding contact portion 47 (as the inclined portion 56 undergoes elastic deformation due to the centrifugal force), and is sandwiched between the inclined portion 56 and the sliding contact portion 47. At the same time, the ring rotating body 13 is pulled down, the holder 11 and the brake ring 61 are sandwiched between the bearing part 12 and the brake shoe 28, and friction pressure is applied to the ring rotating body 13. and the ring rotation traveler l4
Brake the same speed or excessive speed.

By using the above-mentioned material, the brake ring 61 has a surface-hardened smooth sliding contact portion 47 that has frictional resistance,
It is possible to reduce both heat generation and wear.
Following the increase in spindle rotation speed, ring rotating body 1
3 rotation is faster (for example, ring rotation 12,000 to 15,000
1,000 RPM), the temperature rise and wear of the sliding contact portion 47 and the brake ring 61 are extremely low.

In addition, the brake shoe 28 is subjected to engineering pressure against the lower rotor 22 by the presser ring 25, and the protruding line 51a provided on the outer periphery of the vertical portion 51 engages with the engagement groove 22a provided on the lower rotor 22. This acts to prevent removal and integrates the material, but its material properties are as follows:
Properly blend MO3t, Teflon resin, carbon type, silicone oil wax, and other low-friction coefficient wear-resistant additives with urethane-based, fluorine-based rubber, or urethane, polyester, and other high-polymer soft elastic and heat-resistant elastomers. However, when the material of the brake shoe 28 is a composite elastomer, the elasticity and hardness are 80 degrees or less, and when the above-mentioned synthetic rubber is used. (can be as low as 60 degrees ± 10 degrees), and it is extremely easy to mold the elastic hardness to adjust it depending on the purpose of use.

Therefore, as mentioned above, for applications where the brake shoe 28 is required to elastically deform and lift up when the ring rotates around 6,000 RPM and start contact friction, a material with low hardness and high elastic modulus should be selected, for example, a material with a hardness of 70 degrees ± 5 degrees),
For high-speed applications where the brake effect starts to appear when the ring rotates at 8,000 RPM or higher, the hardness may be increased slightly.
(for example, 80 degrees ± 5 degrees) to delay the timing of lift-up and contact of the brake ring 61 due to centrifugal force, or adjust the thickness of the brake ring 61 to be thinner.
By increasing the gap C between the sliding contact portions 47 of No. 1, adjustments such as delaying the timing of contact can be made easily.

In addition, since the engagement groove 62 and the radial protrusion 72 engage and rotate together, the sliding friction caused by the rotation of the brake shoe 28 is concentrated on the upper surface of the sliding contact portion 47 and the brake ring 61. There is no sliding friction between the lower surface and the inclined portion 56 or the support protrusion 71, and the inclined portion 56 is used for lifting the brake ring 61 up and down by elastic deformation due to the centrifugal force of the ring rotating body 13, and for sliding. Since the brake shoe 28 performs a friction braking action by rotating while being pressed against the contact portion 47, no wear damage occurs to the brake shoe 28. Further, since the brake ring 61 is made of a high polymer engineering plastic material or fine ceramic material with a low coefficient of friction and excellent wear resistance and heat resistance as described above, and both sliding friction surfaces are finished as smooth surfaces, Ring rotating body 1
Even when used at high-speed rotation, the temperature rise and wear due to friction are extremely low, making it a highly durable mechanism.

According to the rotating spinning ring 1 of the above-described embodiment, the brake ring 6 due to the rise of the inclined portion 56 of the brake shoe 28
Assuming that the rotation speed of the ring rotating body 13 at the time of contact with the sliding contact portion 47 of No. 1 is 7,000 to 8,000 RPM, the ring rotation should be increased to 10,000 RPM in response to an increase in the torque of the roller due to the subsequent increase in spindle rotation. Since it is possible to set the speed to follow up to ~12,000 RPM, even higher speed spinning is possible than with a brake mechanism in which the brake shoe 28 is brought into direct contact with the sliding contact portion 47.

That is, the standard ring rotation difference with respect to the spindle rotation mentioned above is set to be around 14,000 PPM, the ring rotation speed at the beginning of contact is set to 7,000 to 8,000 PPM, and the upper limit of the ring rotation speed is set to 10,000 to 12,000 PPM. PPM, the spindle rotation increase limit is 24,000 to 26,000 RPM (or 25,000 RPM
) becomes possible.

However, if the frictional resistance between the sliding contact portion 47 and the brake ring 61 is extremely reduced, and the brake shoe 28 is set to a combination of high hardness and low elasticity, if the spindle rotation is decelerated at a steep angle and stopped at a stop. , the ring rotation does not follow the decrease in spindle rotation, and there is a risk of overrun. Therefore, the elasticity of the material of the brake shoe 28 is increased and the hardness is set to 80 to 60 degrees, so that the brake shoe 28 takes the lead and the contact pressure part does not separate even when the spindle rotation is decelerated.
Ring rotation can be reduced to 7 times using multi-stage deceleration using inverter control, etc.
If the power is lowered to 1,000 PPM or less and then 5W10FF is applied, the excessive Snarl phenomenon due to overrun will be resolved.

Note that these condition settings vary depending on the type of spun yarn, yarn count, spinning spindle rotation range, traveling ring diameter, lift, other spinning conditions, and machine performance, but in general,
It is roughly divided into fine/medium capacity and large size, and depending on machine conditions, semi-high speed with a maximum rotation speed of 20,000 PPM or less, and the latest high speed with a maximum rotation speed of 20,000 to 25,000 RPM. Since the rotating ring 1 for spinning is considered to be for spinning machines,
The conditions for the brake shoes 28 and brake ring 61 described above can also be limited to several types of small ranges.

FIG. 4 shows a rotating ring 2 for spinning according to another embodiment of the present invention.
FIG.

In FIG. 4, members having the same functions as those of the rotating spinning ring 1 in FIG. 1 are given the same reference numerals and their explanations will be omitted.

In the brake shoe 29 of this rotating ring for spinning 2, the support protrusion 71 provided on the inclined part 56 of the brake shoe 28 in the above-mentioned rotating ring for spinning 1 is omitted, and instead, the cross section of the tip part is semicircular. A protrusion ring 64 is provided on the lower surface of the brake ring 63, and the cross-sectional shape of the brake ring 63 is T-shaped. Further, the brake ring 63 is not provided with anything equivalent to the above-mentioned retaining groove 62,
The brake shoe 29 is also not provided with anything corresponding to the radial protrusion 72. In other words, the brake ring 63 is
The tip of the protrusion ring 64 is supported by contacting the surface of the inclined portion 57 of the brake shoe 29, and is held in a horizontal state.

In this rotating spinning ring 2, when the ring rotating body 13 rotates, the brake shoe 29 also rotates, and due to the centrifugal force (the oblique part 57 lifts up, the brake ring 6
3 is lifted in the same way.

When the rotation speed of the ring rotating body 13 reaches a certain set value, the upper surface of the brake ring 63 comes into contact with the sliding contact portion 47, and a braking force is generated.

FIG. 5 shows a spinning ring 3 according to another embodiment of the present invention.
FIG. 6 is a partial front view showing the rotating spinning ring 3 of FIG. 5 in a state where a braking force is applied.

In these figures, members having the same functions as the rotating spinning ring 1 in FIG. 1 and the rotating spinning ring 2 in FIG.

The brake shoe 30 of the rotating spinning ring 3 is attached to the vertical portion 5
1. It consists of a bending part 53 and a movable peripheral collar part 58 that protrudes annularly from the bending part 53 in the outer circumferential direction, and the brake ring 65 is supported by the movable peripheral collar part 58 via a lift guide 80, and is horizontally maintained in the state. That is, the lift guide 80 includes a cylindrical vertical portion 80a loosely fitted to the lower outer circumferential surface 22b of the lower rotor 22 with a minute gap, and a movable peripheral flange on the lower surface that extends horizontally from the lower end of the vertical portion 8 (la). 58, and a pull-down hook part 8Qc with an inverted cross-section connected to the outer peripheral end of the collar ring part 80b, and is freely movable up and down using the lower outer peripheral surface 22b of the lower rotor 22 as a slide guide surface. Brake ring 6
5 is the lift distance (
They are fitted onto the upper surface of the collar ring portion 80b so as to face each other with a gap C. Note that the lift guide 80 is, for example,
Manufactured by press molding of aluminum or other metal thin plates.

On the lower surface of the flange ring portion 80b of the lift guide 80, three protrusions 82 corresponding to the engagement grooves 62 of the brake ring 61 in the above-described spinning ring 1 are spaced at equal intervals in the circumferential direction.
On the other hand, on the upper surface of the movable peripheral flange 58, in place of the above-mentioned radial projections 72, the same number of concave diagonal grooves 73 having a downward slope toward the outer periphery are provided at the same intervals as the projections 82. It is being The protrusion 82 and the concave diagonal groove 73 engage with each other in a non-contact manner in a stationary state.

Further, the pull-down hook portions 80C of the lift guide 80 are provided at several equally spaced locations on the outer peripheral edge of the collar ring portion 80b. Surrounds the surface and bottom without contact.

When the ring rotating body 13 rotates, the brake shoe 30 also rotates integrally, and the bending portion 53 is elastically deformed by the upward component of the centrifugal force, and the movable peripheral flange portion 58 is lifted upward. The amount of upward movement of the movable peripheral flange 58 is the same as that of the ring rotating body 13.
The bending fulcrum O becomes larger depending on the rotation speed of O
The angle α at which the line of action connecting the center of gravity of the movable peripheral collar portion 58 intersects with the horizontal plane becomes smaller as the rotational speed increases.

Due to the upward movement of the movable peripheral flange 58, the upper plane part of the movable peripheral flange 58 first pushes up the lower surface of the flange ring 80b of the lift guide 80, and then the concave diagonal groove 73 protrudes from the lower surface of the flange ring 80b. Push up the raised protrusion 82. lift guide 8
0 moves upward along the lower outer circumferential surface 22b of the lower rotor 22 while rotating integrally with the ring rotating body 13 in a state where the protrusion 82 and the concave oblique groove 73 are engaged and in contact with each other,
Lift up the brake ring 65.

Furthermore, as the ring rotation speeds up and the upper component of the centrifugal force increases, as shown in FIG.
The circular arc portion on the upper edge of the outer periphery pushes up the lower surface of the collar ring portion 80b, and the brake ring 65 comes into contact with the sliding contact portion 47 of the holder 11 and is pressed.

As a result, a frictional force is generated between the brake ring 65 and the sliding contact portion 47, and a braking force is applied.

Brake ring 65 depending on the rotation speed of ring rotating body 13
The pressing force against the sliding contact portion 47 increases, and the braking force also increases.

As the spindle rotation decreases, the ring rotational torque decreases, and the ring rotation speed decreases, the upper component of the centrifugal force also gradually decreases, and when the ring rotation speed drops to around 6,000 rotations, the brake ring 65 moves together with the lift guide 80. It descends and leaves the sliding contact portion 47. When the lift guide 80 is lowered, the movable peripheral collar part 5 pushes down the pull-down hook part 80c of the lift guide 80 with its outer peripheral lower end, and quickly moves the brake ring 65 to the height of the rest position shown in FIG. It acts to bring it back.

According to this rotating spinning ring 3, by providing the lift guide 80 having the vertical portion 80a, the center runout of the brake ring 65 due to rotation is prevented, and the braking action is stabilized.

In addition, by increasing the weight of the movable peripheral flange 58, it is possible to increase the pressurizing braking force due to the upper component of the centrifugal force, so that the ring rotation speed can be increased, and the ring rotation during large-count spinning, etc. It is also compatible with rotating rings with larger torque, and the range from when the ring starts contact at around 6,000 rotations to the maximum braking rotation speed is 400 rotations.
Since it is possible to adjust the range from 0 to 6000 PPM,
The ring rotational speed change curve can more closely follow the spindle rotational speed change curve, and isolation of both rotational speeds can be further reduced. Furthermore, it is possible to increase the push-up distance of the brake ring 65, and it is possible to easily adjust the thickness of the brake ring 65 and adjust the gap C between the brake ring 65 and the sliding contact portion 47. I can do it.

According to the embodiment described above, the braking force is applied when the rotational speed of the ring rotating body 13 reaches a certain value, so that the spinning tension control effect, which is the most important feature of the passive rotating ring, is not impaired, and the generation of fuzz is prevented. This prevents the occurrence of white powder drop, wrinkles, yellowing of melted yarns, weak yarns, and other deterioration of yarn quality that occur during high-speed spinning of heat-fusible fibers such as pure synthetic fibers and high-ratio blended yarns. Furthermore, by preventing the ring rotating body 13 from rotating at an excessively high speed, inertial rotation due to its inertia is suppressed, and as a result, when the machine is stopped, the rotation of the ring rotating body 13 is stopped before or at the same time as the spindle stops. This prevents the occurrence of snarl due to overrun of the ring rotating body 13.

In addition, according to the above-mentioned embodiment, it is possible to adopt a brake that sets the maximum ring rotation, so that the traveler can
Since it does not rotate at the same speed as the rotation or rotate at an excessively high speed, the bearing part 12 is made of wear-resistant high engineering plastic without requiring complicated mechanisms such as rolling bearings or air bearings or other power. Since it uses a sliding friction bearing and can withstand long-term use, it has a simple structure, is inexpensive, and can reduce power consumption.Moreover, it does not require modifying the spinning machine (by replacing the ring itself). It is possible to use.

According to the embodiment described above, it is possible to prevent the individual weight rings from becoming the same speed as the traveler and to raise the ring maximum rotation limit. In order to prevent abnormal fluctuations in the spinning tension caused by synchronizing the ring rotation with the maximum rotation of the traveler between chases during the spinning process, which did not solve the problem, the maximum rotation of the individual weight rings was adjusted to maintain an appropriate rotation difference from the traveler rotation. can be controlled. Moreover, a separate power source is not required for the rotation of the ring rotor 13 and the brake operation, and the energy required for the rotation of the ring rotor 13 can be converted from the energy of wear and burnout of the traveler 14 to the traveler 14. - The replacement cycle of the traveler 14 is extended by 2 to 3 times by reducing burnout. And Traveler-14
As a result of converting the micro-vibration of the spindle and the spinning stroke into ring rotational energy, the fluff of the spinning yarn is reduced by one-third to one-fifth in terms of yarn count.

According to the embodiment described above, the spinning spinning ring 12.3 has:
It has a simple structure, can be manufactured at low cost, does not require expensive modification of the machine, and has extremely high economic efficiency.

In the embodiments described above, various structures may be employed for the structure of the bearing portion 12, the connection structure between the flange rotor 21 and the lower rotor 22, the structure for attaching the brake shoes 28, 29, 30 to the ring rotating body 13, etc. I can do it. The position of the protrusion ring 64 formed on the brake ring 63 may be moved to the inner circumferential side or the outer circumferential side, and its cross-sectional shape may be changed to an inverted letter shape or the like. Alternatively, the protrusion ring 64 formed on the brake ring 63 may be omitted, and the inner lower end edge of the brake ring 63 may be in contact with the surface of the inclined portion 57.
In this case, by forming the inner lower end edge of the brake ring 63 into a smooth arc shape, the brake ring 63 can be smoothly moved up and down.

Furthermore, the sliding contact portion 47 on the lower end surface of the holder 11 is made into a tapered surface that slopes outward and downward, and the upper surfaces of the brake rings 61, 63. By making it a tapered surface having the same angle as the sliding contact part 47, or by making the upper surface of the sliding contact part 47 and the brake rings 61, 63° 65 into an arc shape,
The frictional pressure applied to the sliding contact portion 47 may be increased.

In the above embodiment, the brake shoe 28.29.3 has the vertical portion 51, the bent portion 53, and the inclined portion 56.57 or the movable peripheral collar portion 58 integrally formed of synthetic resin or the like.
0 has been described, but its configuration can be changed in various ways. For example, as shown in FIG. 7, the bent portion 53 is formed by an elastically deformable plate spring 90, and the bent portion of this temporary spring is used to form a vertical portion 51 made of synthetic resin or the like and an inclined portion 56, 57 or a movable portion. By connecting the peripheral flange 58 and easily adjusting the spring elasticity uniformly depending on the hardness and plate thickness of the temporary spring 90, the lifting function of the inclined portion 56, 57 or the movable peripheral flange 58 due to centrifugal force can be improved. It may be configured to meet the design purpose. In addition, the structure, shape, size, material, etc. of each part can be changed in various ways other than those described above.

[Effects of the Invention] According to the present invention, excessive speeding up of the ring rotating body, particularly synchronization with the maximum rotation of the traveler rotation, is prevented.

Therefore, it is possible to control the maximum rotational speed of each weight ring so that a rotational difference that does not cause the ring rotational speed change curve to deviate excessively from the spindle rotational speed change curve can be maintained. In addition, it limits the increase in the ring rotation speed,
Since excessive speed increase can be suppressed, it is possible to eliminate overrun and excessive snarl phenomena caused by ring inertia rotation when stopped. Furthermore, it becomes possible to significantly increase the rotational speed of the spindle, contributing to improved productivity.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional front view of a rotating ring for spinning according to the present invention;
2 is a partially sectional front view showing the main parts of the spinning ring shown in FIG. 1, FIG. 3 is a partial front view showing the spinning ring shown in FIG. Figure and 5th
The figure is a cross-sectional front view of a rotating ring for spinning according to another embodiment of the present invention, FIG. 6 is a partial front view showing the rotating ring for spinning shown in FIG. 5 in a state where a braking force is applied, and FIG. 7 is a brake FIG. 7 is a partially sectional front view showing a modified example of the shoe. 1.2.3... Rotating ring for spinning, 11... Holder, 12... Bearing part, 13... Ring rotating body, 28
29.30...Brake shoe, 47...Sliding contact part,
61.63.65...Brake ring.

Claims (1)

[Claims] (1) In a rotating ring for spinning comprising a holder and a ring rotating body rotatably supported by the holder via a shaft bearing, a brake shoe made of an elastic body is provided at the lower end of the ring rotating body. and a brake ring supported by the brake shoe, the brake shoe is deformed by centrifugal force due to rotation of the brake shoe, and the brake ring is attached to the lower end surface of the holder due to the deformation of the brake shoe. A rotating ring for spinning, characterized in that it is configured to come into contact with a sliding contact portion provided therein.